Hydraulic pump



' Sept. 13, 1949. H. A. w. PETERSEN HYDRAUL I C PUMP 3 lSheets-Sheet 1 Filed July 2, 1948 Arras/Veys.

Sept. 13, 1949. H. A. w. PETl-:RsEN

HYDRAULIC PUMP s sheds-sheet z Filed July 2, 1948 1N V EN TOR. Hf INPI C H A. Ml. PErERSEM Sept' 13 1949- H. A. w.'PE'rERsEN 2,481,613

HYDRAULIC PUMP Filed July 2, 1948 s sheets-sheet s INVENTOR. Hf//V/C W FETIHSEIV,

Patented Sept. 13, 1949 UNITED STAT HYDRAULIC PUMP Heinrich A. w. Petersen, Fort Myers, Fn., ee-

signor to Petersen and Kelley Corporation, Berkeley, Calif., a corporation of Delaware Application July 2, 1948, Serial N0. 36,771

vs claims. l

This invention relates to improvements in hydraulic pumps and more particularly to an improved multi-stage rotary pump for handling liquids such as water, oil, etc.

It is among the objects of the invention to provide an improved multi-stage rotary pump, the eiliciency of which. is greatly increased over the v emciency'of conventional rotary pumps by the Figure i is a longitudinal medial cross-section through a pump illustrative of the invention, the cross-section being taken on a substantially horizontal plane.

Figure 2 is a transverse cross-section taken substantially on the line 2--2 of Figure 1.

Figure 3 is a transverse cross-section taken substantially on the line 3-3 of Figure 1.

Figure 4 is a. longitudinal, medial cross-section on an enlarged scale of one of the end bearings of the pump.

Figure 5 is a. longitudinal medial cross-section v-on a substantially vertical plane of the pump bearing illustrated in Figure 4.

Figure is a transverse cross-section of a. frag- Y mentary portion of a pump bearing taken substantially on the line 'Ii-6 of Figure 5.

With continued reference to the drawings, the improved pump comprises, in general, a two part housing I0, a composite rotor I I mounted on a pump shaft I2, which extends longitudinally through the housing I and is journaled in the end bearings I2 and I3 and a pair of thrust bearings Il and I surrounding the pump shaft in the housing I0.

The housing I0 comprises two symmetrical, substantially semi-cylindrical portions providing an upper portion I6 and a lower half or portion I1. The 'two portions I6 and I1 are provided with outwardly extending marginal flanges I8 apertured to receive bolts I9 spaced apart around the housing to firmly secure the two parts together, a suitable gasket preferably being interposed between the flanges to render the hous- 2 ing leak-proof. .An intake conduit 2l extends tangentially from the lower portion I1 of the housing near one end of the latter and an outlet conduit 22 extends tangentially from the same lower portion of the housing near the midlength location thereof. Both of these conduits are provided on their outer ends with respective annular flanges 23 and 24 for the attachment of suitable pipe lines or other conduits thereto. It will be noted from an inspection of Figures 2 and 3 that both the inlet and the outlet conduit enter the lower portion I1 of the housing near the bottom of the latter. `The two housing parts I5 and Il have somewhat tapering end portions and provide, when operatively connected together, an lnternal cylindrical main chamber 25 and a circular intake chamber 26 separated from the main -chamber by an internal annular wall 21 having a thrust bearing retaining ribs and thrust bearings disposed one at each end of the main pump chamber retain liquid in the chamber and render the pump self-priming.

'I'hc pump shaft I2 extends coaxially through the chambers 25, 25. 28 and 3i through the thrust bearings I4 and I5, throughthe ends of the housing III and through the shaft bearings I 2' and I3 disposed one at each end of the housing. The ends of the shaft-receiving bore in the housing are counter-bored to receive respective packing assemblies 34 and 35. Each of these packing assemblies includes a body 36 of packing material in the inner end of the respective counter-bore, a packing gland 31 received in the outer end of the counter-bore and secured to the corresponding end of the housing by cap screws 38 which are elective, when tightened, to move the associated packinggland inwardlyvoi the housing to com- -press the packing material in the conventional manner.

The shaft bearing I2' comprises a substantially semi-cylindrical housing l0 spaced from the ad` jacent end of thevmain housing III 'and'secured thereto by a strut II of semi-conical shape provided with suitable opening to provide access to ing housing 40 is provided internally with a sub-k stantially central boss having in its upper surface a partly spherical seat for the semi-spherical, self-aligning bearing bushing 4I. This bearing bushing is provided with a central groove 42 and with semi-cylindrical end portion having grooves 43 which grooves receive respective oiler rings 44. The bearing bushing 4I is provided with a shaft receiving bore which has a lining 45 of suitable bearing material, such as Babbitt metal or bronz, The upper half of the self-aligning bearing is provided with slots in the corresponding grooves 42 and 43 so that the oiler rings 44 lie on the top of the shaft and carry oil from the bottom of the lowerv housing portion I2' to the top of the shaft for distribution through the bearing. An oil slinger washer 46 is secured on the shaft adjacent the inner ends of the bearing bushing to prevent leakage of oil through the shaft receiving aperture in the inner end walls of the upper and lower bearing housing parts. Each bearing housing part is also provided internally thereof -with apertured lugs 4l extending inwardly from its side walls, the apertures in the lugs of the lower portion of the housing preferably being internally screw-threaded to receive end boltsI which secure the two portions of the bearing housing together.

The front bearing I3 is illustrated in detail in Figures 4, 5 and 6 and is substantially identical with bearing I2 except that bearing I3 is especially constructed for the passage of the shaft the lower part of lower housing portion 48 to l the shaft. The'lower boss .53 is provided with a medial groove 62 receiving the middle oiler ring 6I and with a transverse oil passage 63 connecting the bottom of the groove 62 with the lubricant-receiving chambers in each end portion ofl the bearing housing. Lubricant is supplied to the interior of the housing through apertured bosses 64 on the top wall of the upper housing I2 entirely therethrough to receive on its outer end one part 48 of a flexible coupling by means of which a driving motor is operatively connected to the pump shaft.

The housing of the bearing I3 comprises a lower semi-cylindrical portion 49 and an upper semi-cylindrical portion 50 fltting upon and secured to the lower portion 49. The lower portion is secured to the corresponding end of the main housing by a suitable strut 5I of semi-conical shape having openings 52 therein providing access to the cap screws 38 of the front packing assembly 35. This part of the housing has in its bottom an upstanding boss 53 having in its upper surface a partly spherical seat for the lower, semi-spherical portion 54 of the substantially spherical self-aligning bearing bushing, generally The upper portion 50 of the indicated at 55. bearing housing is detachably secured to the lower portion 49 by bolts extending through apertured lugs provided internally of the upper portion and threaded into internally screwthreaded apertures or wells provided in corresponding lugs 56 provided in the lower portion 49 of the bearing housing-and is provided ini ternally with a downwardly extending boss 51 projecting from the top wall thereof and providportion and a .suitable abutment bolt 85 extends through the center of the upper housing portion boss 51 into a'suitable opening in the top of the upper bearing bushing 58 to prevent the bearing bushing from rotating in the housing while providing suilicient freedom of movement of the bushing in the housing for self-aligning purposes.

'I'he two parts of the bushing are secured together by fastening elements such as Allen screws operatively disposed in registering openings 66 provided in the upper and lower parts of the bushing. Within the housing and near the opposite ends thereof the shaft I2 is provided with a pair of spaced-apartannular grooves each pair providing between them an oil slinger ring 61 to prevent the lubricant from owing out of the bearing housing around the shaft, and similar rings 68 are provided on the shaft within the flanged end portion 68 of the two part bearing bushing 65. The two parts of the bearing bushings are provided with liners 'I0 of suitable bearing material, such as Babbitt metal or bronz, around the shaft-receiving bore in the bushing and adequate lubricant is supplied to these linings by the oiler ringsSI, as is clearly apparent from an inspection of Figure 5. An annular ring or shoulder 1I is provided on the shaft between the bearing I3 and the packing assembly 35 to prevent any liquid from the pump from flowing along the shaft and into the bearing.

The pump shaft' I2 is accurately journaled in the housing I0 by means of the two bearings I2 and I3, and is sealed to the housing against leakage by the packing assemblies 34 and 35.

The pump rotor I I is secured on shaft I2 within the cylindrical pump chamber 25 and comprises a substantially cylindrical outer casing and a number of internal impellers equal to the number of pump stages desired.

The casing 12 of the pump rotor is made up of several parts for convenience in manufacture and assembly. In the arrangement illustrated, there are three parts including a rear part, an intermediate part and a front part. The rear part has a circular rear wall 13 provided with a central aperture 14 constituting an inner passage for liquid into the rotor, and an annular wall 15 extending forwardly from the outer edge of the end wall and provided in its front edge with an annularA groove. The intermediate portion comprises a circular wall 'I6-having a central aperture 11 providing a fluid passage from the rst to the second stage of the pump and has an annular wall 'I8 peripherally of the circular intermediate walls 16 which annular wall-is lprovided on its rear edge with an annular tongue received in the groove in the front edge of annular wall 15 of the rear portion and.'l in its front edge with an annular groove receiving an annular tongue provided on the rear edge of the front portion of the rotor. The front portion of the rotor comprises a circular inner wall 19 provided with a. central aperture constituting a fluid passage from the second to the third or final stage of the pump, with a thick outer front end seated in the front end groove of the annular.

wall 18. Between the adjacent surfaces of the walls 18 and 8| the annular wall 82 is provided with a slot 83 through which the fluid passes'from the pump rotor into the main chamber 25. From the main chamber, the fluid passes through the outlet conduit 22 which extends from the housing and communicates at its inner end'with the main pump chamber. Within the cylindrical sure ring 88. An annular rib 82 is provided' on the outer surface of rear rotor wall 13 surround-y ing the corresponding end of inner bearing memy' secured to the shaft against relative rotation by Y. a suitable-key 84. Itwill be 'noted that the key if 84 .isl somewhat vshorter than the hub so that casing 12 are'two circular impeller walls 84 and 85, respectivelyV positioned adjacent to the rear end wall 13 and the intermediate wall 16 but spaced therefrom. g

These impeller walls are provided with lcentral apertures closely receiving the corresponding portion of the shaft I2 and are secured to the shaft against rotationv relative thereto by vsuitable means, such as the Woodruff keys 86. A similar Woodruff key also preferably connects the front wall 8| with the pump shaft. Impeller blades or vanes 81 are disposed transversely of the space vbetween each impeller wall 84 and 85 and the corresponding rear wall 18 and intermediate wall 18 and between the front wall 8| and the inner front wall 18. These impeller blades are preferably formed integrally with the walls at the opposite sides of the spaces in which they are provided and-are preferably spirally curved, as illustrated in Figure 2, in conventional form.

With the above construction the entire rotor is rotated by the shaft in the main chamber 25 of the pump and as it rotates liquid flows in through the rotor inlet opening 14 adjacent the shaft, is forcedradially outwardly by the first set of impeller blades or vanes into the space between impeller wall 8| and intermediate'wall 16 from which it flows to the second stage through intake opening 11 and is again forced radially outwardly by the impeller blades 81 disposed between the impeller wall 85 onl the intermediate wall 16 into the space between the impeller wall 85 and inner front end wall 18 from which it flows through the inlet opening 80 into the space between the inner and outer end wall 18 and 8| and is forced radially outwardly by the corresponding impeller blade and discharged through the space between the outer edges of the front end wall 8| and the annular wall 82. The velocity of the uid is thus built'up in several stages in the rotor and the iiuidis discharged at high velocity from the rotor into the main pump chamber 25 where its dynamic energy or momentum is converted into hydraulic pressure for discharge of the -liquid at high pressure through the outlet conduit 22. y

The thrust bearing i4 comprises an annular ring 88 of somewhat U-shaped cross-sectional shape having. an outwardly opening annular groove receiving the' bearing retaining rib 28 provided by the two portions of the main housing.

A pressure ring 88 of right 'angle cross-sectional shape has its cylindrical portion closely fitting the inner surface of the annular wall of the retaining ring 88 and its annular flange bearing upon the outer surface of theA flanged inner end of the ring 88. An inner bearing member 80 has an elongated cylindrical portion journaled in the cylindrical portion ofthe pressure ring 88 and extending inwardly into contact with the outer surface of the rear end wall 13 of the -rotor and has a thickened annular flange 8| bearing on the outer surface of the annular flange of the presber 80 to maintain this member centered relative to the aperture 14. Thel inner bearing member 80 also includes a cylindrical hub received on the reduced rear end portion of the shaft l2 and leakage of fluid will not occuralong this key. Hub 83 is connected to the cylindrical portion of the inner member by suitable angularly spaced spokes 95, as particularly illustrated in Figure '8.

With the above arrangement,- fluid entering the front intake chamber 26 through the .intake conduit 2| flows through the space `88 between the cylindrical portion of the inner bearing member 80 and the hub 83A thereof to the rotor inlet opening 14 in the rear wall 13 of the rotor. Liquid under pressure can leak from the main chamber into the intermediate chamber 28 but cannot leak in any important quantity past the thrust bearing I4 to the inlet chamber 26 as the annular flanges of the thrust bearing members 88, 88 and 80 are held together with suiiicient pressure to preclude any important leakage of fluid through the bearing. lAny insignificant amount of fluid leaking through lubricate the bearing and returns to the inlet chamber 26 from which it is again fed into the pumpv rotor. The outer and inner parts 88 and l of the thrust bearing are preferably formed of a suitable bearing material, such as bronz, and the intermediate portion 88 of a hard material such as stainless steel or tool steel to provide good bearing lsurfaces between the three parts of the bearing. As the intermediate part is rotatable relative to both the inner part and the outer part, ,the rotational speed between contacting bearing surfaces 'of the thrust bearing is greatly reduced thereby contributing to long life and satisfactory service of the bearing.

The thrust bearing lI5 is interposed between the main lpump chamber 25 and the leakage chamber 8| and comprises an outer ring of U or channel shaped cross-section'having an outwardlyv opening intermediate groove receiving the bearing retaining rib 33 of the pump housing at the front end of pump chamber 25, an intermediate pressure ring 88 of right angular cross-section and an inner ring |00 having a cylindrical portion journaled in the cylindrical portion of the pressure ring 88 and a thickened annular flange |0l bearing upon the outer surface of the annu# lar flange of the pressurering. The outer and inner rings of each bearing are preferably formed:

of a suitable bearing material, vsuch as bronz.

and the intermediatev pressure ring 88 is formed of a hard material such as stainless or tool steel to provide suitable bearing surfaces.

The inner ring |0|ll is provided with .a centri-il aperture which closely fits the shaft l2 and is held against forward longitudinal movementvon the shaft by an abutment ring oriiange |02 vprovided on the shaft. Any liquid leaking from the pump chamber 25 through bearing |5 to the leak,`

-age'chamber 3| is returned through a suitable conduit |03 to the intake conduit 2| of the pump. No important quantity of liquid can leak through the improved thrust bearing however, the .amount of leakage being onlysuflicient'to lubricate the` bearing.

The parts of the rotor are firmly held to" gether and the inner ring 80 of the 'thrust bear-Q this thrustV bearing serves to spects as illustrative and I chamber ing I4 is held in operative assembly with-the rotor y by a tubular sleeve |04 which surrounds the reduced end portion of shaft |2 between the rearward end of the hub 93 of inner ring 90 and abutment washer |05 which surrounds the rear end ofthe shaft and is forced against the end of sleeve |04 by a nut |06 threaded onto the externally screw-threaded rear end of the shaft. When the nut is tightened the inner ring of the thrust bearing 5 is forced against the annular shoulder |02 and the inner ring of thrust bearing I4 is forced against the rear wall of the rotor so that the rotor, the inner rings of the two thrust bearings and the sleeve are all rigidly `assembled on the shaft and secured against rotation relative thereto.

By rotating the outer casing Il of the rotor with the rotor impellers, a leak proof connection can be made between the various stages'of the pump so that no liquid will leak back from a higher to a lower stage thus decreasing the emciency of the pump. The improved pump is thus highly emcient, is simple in construction and extremely .easy to assemble, avoids any leakage of liquid around the pump shaft and is extremely durable in use.

The invention may be embodied in other specicforms without departing from the spirit or essential characteristics thereof. The present embodiment is therefore, to be considered in all renot restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed is:

l. A multi-stage, rotary hydraulic pump comprising a hollow housing having a cylindrical pump chamber therein and two secondary chambers disposed one at each end of said pump chamber and separate therefrom, one of said secondary chambers being larger than the other and constituting an intake chamber for said' pump and the other of said secondary chambers constituting a leakage chamber, means hydraulically connecting the leakage chamber to the intake chamber, a pump shaft extending through said housing, a rotor on said shaft within said pump chamber, two self-aligning bearings disposed one at each end of said housing rotatably supporting said shaft, two thrust bearings within said housing disposed one at each end of said pump chamber and operatively interposed between said shaft and said housing, an intake conduit extending through said housing to said inlet chamber, and an outlet conduit extending from said pump through said housing, said rotor comprising an outer cylindrical casing rotatable with said shaft and impellers in said casing. A2. A multi-stage rotary hydraulic pump'comprising a hollow housing having a cylindrical pump chamber therein and two secondary chambers disposed one at each end of said pump chamber and separate therefrom, one of said secondary chambers being larger than the other and constituting an intake chamber forsaid pump and the other of said secondary chambers constituting a leakage chamber, means hydraulically connecting the leakage chamber to the `intake chamber, a pump shaft extending through said4 housing, a rotor on said shaft within said pump chamber, two thrust bearings within' said housing disposed one at each end of said pump chamber and operatively interposed between said shaft and.

zio

8 said housing, an intake conduit extending-through said housing into said inlet chamber, and an outlet conduit extending from said pump chamber through said housing, said rotor comprising a rear end wall, an intermediate wall, an outer front end wall, an inner front end wall, a multipart annular said endwalls and said intermediate walls and having a circumferential opening therethrough between said outer and inner front end walls, two impeller walls disposed one adjacent said rear end wall and one adjacent said intermediate wall, and impeller vanes ldisposed between said rear end wall and said intermediate wall and the respective impeller walls and between said outer and inner front end walls.

3. A multi-stage rotary hydraulic pump comprising a hollow housing having a cylindrical pump chamber therein and two secondary chambers disposed one at each end of said pump chamber and separate therefrom, Ione of said secondary chambers being larger than the other and constituting an intake chamber for said pump and the other of said secondary chambers con-l stituting a leakage chamber, means hydraulically connecting the leakage chamber to the intake chamber, a pump shaft extending through said housing, a rotor on said shaft within said pump chamber, means supporting said shaft for rotation in said housing, two thrust bearings within said housing disposed one at each end of said pump chamber and operatively interposed between said shaft and said housing, an intake conduit extending through said housing to said inlet chamber, and an outlet conduit extending from said pump chamber through said housing, said rotor comprising a cylindrical outer casing secured on said pump shaft and providing at one end a liquid inlet opening around said shaft and at its opposite end acircumferential liquid outlet opening, and at least one impeller in said casing rotatable therewith.

4. A pump shaft and rotor assembly comprising a shaft having an annular shoulder thereon and a reduced end der, a cylindrical casing having a front wall surrounding and closely tting said shaft and bearing against said shoulder, a rear wall having a shaft receiving opening larger than said shaft, a multi-part annular wall surrounding said shaft between said front wall and said rear wall', internal walls and pump vanes within said casing, a.

bearing ring having a cylindrical hub receiving' the reduced portion of said shaft and an outer cylindrical wall annularly spaced from said hub and connected thereto by radial spokes with said outer wall bearing at one end against said casing rear wall and surrounding the shaft receiving opening in the latter, a cylindrical sleeve receiving the reduced portion of said shaft bearing at its inner end against said hub, and a nut threaded onto said shaft of said sleeve ing ring and and bearing against the outer end said sleeve between saidshoulder and said nut.

5. A multi-stage, rotary hydraulic pump comprising a hollow housing having a cylindrical pump chamber therein and two secondary chambers disposed one at each end of said pump chamber and separate therefrom, one of said secondary chambers being larger than the vother and constituting an intake chamber for said pump and the smaller of said secondary chambers constituting a leakage receiving chamber, a pump shaft extending through said housinga rotor on said wall extending peripherally aroundportion spaced from said shoul` to compress said rotor, said bear-A The following references are of record in the REFERENCES crrED le of this patent:

UNITED STATES PATENTS Number Name Date Noble June 9, 1925 Spiilmann et al. i--- July 3, 1928 

